Hydraulically actuated air compressor



- J -1. 7, 1961 c. M. 'RI'URSKY 2,968,434

I HYDRAULICALLY ACTUATED AIR COMPRESSOR Fil ed Jan. 2a, 1958 I 2 Sheets-Sheet 1 HTTORNEY r 36 INVENTOR.

Cmemfj M 717/?5/0 50 BY I HYDRAULICALLY ACTUATED AIR COMPRESSOR Charles M. Tursky, 542 Broad Ave., Palisades Park, NJ.

Filed Jan. 28, 1958, Ser. No. 711,706

17 Claims. (Cl. 230--57) Still more particularly, the invention deals with a 3 structure of the character described, wherein each, of the cylinder units are so mounted in connection with the rotor casing as to be adjustable one with respect to the other in cont-rolling the positioning of the units with respect to operation of the rotor in controlling the efiiciency in operation of the pair of air compressor units.

The novel features of the invention will be best understood from the following description, when taken together with the accompanying drawings, in which certain embodiments of the invention are disclosed and, in which, the separate-parts are designated by suitable reference characters in each of the views and, in which:--

Fig. 1 is a substantially central sectional view roughly on the line 1--1- of Fig. 2, with parts of the construction shown in elevation and with parts broken away.

Fig. 2 is a section roughly on the broken line 22 of Fig. 1, showing one of the air compressor cylinder units in longitudinal section and the drive of the other unit in central cross-section, with parts of the construction broken away.

Fig. 3 is an enlarged detail view of part of the construction shown in Fig. 2 to more clearly illustrate showings which are diagrammatically illustrated in Fig. 2 and with other parts broken away and in section.

Fig. 4 is an exploded view of the central and one end portion of the three blades of the rotor, illustrated in plan in Fig. l of the drawing.-

Fig. 5 is an enlarged detail view of a portion of one of the. valve structures employed, as it appears 'when not in use; and

Fig. 6 is a sectional view through the edge portion of one of the valves shown in Fig. 5, illustrating the same in use, the sectional view of Fig. 6 being an enlargement of one corner portion of the large diameter cylinder and head of one of the cylinder units.

Considering Figs. 1 and 2 of the drawing, 10 reprecents a central hydraulic cylinder, to the lower portion of which are suitably attached widespread supporting legs 11, indicated in part in both figures. At 12 and 12' are illustrated, in Fig. 2 of the drawing, two similar air compressing cylinder units adjustably supported upon the cylinder 10 'by a plurality of equally spaced bolts 13. By reason of this equal spacing, the units 12, 12' can be positioned at different stations with respect to the cylinder 10,. as will be apparent.

Arranged between the units 12, 12' and the side surfaces of the cylinder 10 are ground facing plates 14, 14', which close the sides of the cylinder 10, as will clearly appear from a consideration of Fig. 2 of the drawing.

2,968,434 Patented Jan. 17, 1961 The units 12, 12' have, centrally thereof, housing portions 15, 15' which extend into and abut the plates 14, 14' and have threaded apertures 16, 16 at their outer ends for reception of closure plates 17, one plate 17 only being illustrated arranged in the aperture 16', it being understood that a similar plate is adapted for mounting in the aperture 16.

The housing portions 15, 15 are generally circular in form and are spaced from outer walls of the units 12, 12 to form air circulating passages 18, 18 having an admission port 19, note Fig. 1, for admitting air, under atmospheric pressure, to the passages 18, 18, these passages intercommunicating in the passage 20 in the cylinder 10 and communicating with the apertures 21, 21' in the plates 14, 14, as clearly noted at the bottom of Fig. 2 of the drawing.

Returning now to the cylinder 10, this cylinderhas a bore 22 and eccentrically arranged in the bore 22 is a rotor-23, comprising two substantially similar rotor discs 24, 14, having a tongue and groove peripheral engagement, as indicated at 25 in Fig. 2 of the drawing.

The rotor discs 24, 24' are secured together by equally spaced bolts 26 and these rotor discs have a central aperture 27, in which overlapping and interfitting central portions 28, 29 and 30 of three blade elements 31, 32 and 33, respectively operate. These elements are shown in exploded detail, in part, in Fig. 4 of the drawing, it being apparent that thecentrally located element 32 has its-central portion 29 located centrally; whereas, the elements 31 and 32 are located at outer sides, so that, when these elements are arranged one directly upon the other, these central portions 28, 29 and 30 would collectively form the equivalent of the shank portions 34, 35 and 36 of the elements.

At the outer ends of the blade elements are enlarged blade portions 37, 38 and 39, the outer surfaces of which are ground to fit snugly in the bore 22 of the cylinder 10. For this purpose of grinding, the blades have centrally alined apertures 40 which will facilitate alignment of the blades in a collective grinding operation for accuracy in fit in the bore 22.

The blade portions 37, 38 and 39 operate radially in apertures 41 in the periphery of the rotor 23, the apertures having angularly ofiset enlargements, as at 42, so as to provide free access of a hydraulic medium admitted into the'cylinder 10 under pressure through the admission or intake port 43 to an extended surface of the blade portions 37, 38 and 39 to eifectively drive the rotor in the cylinder 10.

It will he noted, from a consideration of Fig. 1 of the drawing, that the blade portions of the elements 31, 32 and 33 are offset one with respect to the other so that one surface of each blade end is in common alinement with each other.

Considering Fig. 1 of the drawing, it will appear that, starting at 44 directly opposed to the intake 43, the bore 22 has a circumferentially extended groove 45 which extends to a position 46 widely spaced with respect to the admission port 43 and communicating with the groove 45 is an exhaust or discharge port 47, through which the hydraulic medium can be returned to the source of supply to again be placed under the required pressure by suitable means, not shown, for re-charge to the admission port 43 for drive of the rotor 23.

From the foregoing, it will be apparent that, promptly upon utilizing its energy, the hydraulic medium is released and discharged through the exhaust, thus avoiding any build-up or back pressure which would have the breaking action upon the drive of the rotor by the initial injected hydraulic medium.

It will appear, from the foregoing, that, as the rotor 23 is driven by the hydraulic medium, the rotor moves on the blade portions 37, 38 and 39 which operate in the apertures 41, due to the eccentricity of the rotor.

It will appear, from a consideration of Fig. 2,;that, in this section, the part of the groove 45, as at 44, has been omitted in order to clearly show the plate portion in full engagement with the 'bore 22 and with the sides of the blade portion engaging the adjacent surfaces of the plates 14, 14 and, in this showing, one of the enlargedportions 39 of the blade 33 is illustrated in position.

Returning now to the units 12, 12', it will appear, from a consideration of Fig. l of the drawing, that these units are arranged at 90 to each other and, while a longitudinal section is shown through only one of the units, namely the unit 12, it will be apparent that the other unit is of similar construction, thus the brief description of one will apply to the other and, insofar as the other unit is shown, like references will be primed on like parts.

Considering now the unit 12, it will appear that the unit has opposed small and large diameter bores 48 and 49 having sleeve liners 50, 51.

At 52 is shown a piston assemblage, part of the companion assemblage being indicated at 52 at the left of Fig. 2. The piston assemblage 52 has, at its ends, a small diameter piston 53 and a large diameter piston 54, these pistons joining in a central bearing portion 55, 55, having a tapered bore for a tapered bushing 56, .56 forming a bearing support for a crankpin 57, 57', having aball end 58, 58'.

The pin 57, 57 has a lubricating bore 59, 59' for extending lubrication to the bearing 56, 56' and also to the ball end 58, 58, a plug 60, 60' closing the outer end of the bore 59, 59'.

It will appear that the caring portion 55, 55' has an annular passage 61, 61 around the bearing 56, 56, which opens into each of the pistons 53, 54, as clearly indicated in Fig. 2 of the drawing, so that air can be transmitted from the chamber 62 of the piston 54 to the chamber 63 of the piston 53 in operation of the apparatus, as later described.

The discs 24, 24' have extended bearing portions 64, 64', having half-round sockets for reception of one half of the ball ends 58, 58, as clearly appears from a consideration of Fig. 2 of the drawing, and bearing plates 65, 65' are coupled with the bearing portions 64, 64 by bolts, one of which is indicated at 66, the plates being fashioned to seat upon the balls 58, 58' in retaining the same in position and these plates have outer enlargements of their bearing apertures, as indicated at 67, 67 for clearance of the crankpin 57, 57' in the swinging movement thereof, this clearance being quite apparent from a consideration of the crankpin 57 in Fig. 2 of the drawing.

The plates 65, 65', as well as the bearing portions 64, 64', are fashioned to receive ball bearings 68, 68, which are arranged upon outer surfaces of the plates 14, 14 and in the housing portions 15, 15' for free rotation of the rotor 23, when driven by the two crankpins 57, 57.

Mounted on the large diameter bore end 49 of the unit 12 is a head 69 supporting a valve plate 70 on said end of the unit, the head 69 having an annular passage 71 on its inner surface registering with spaced apertures 72 in the plate 70, only two of which apertures are shown. It will also appear that the head 69 has a by-pass aperture 73, which registers with the chamber 18 or a passage 74 opening into said chamber, so that air is free to extend into and through the apertures 72 into the outer end of the large diameter cylinder, this admission of air being controlled by a springring valve assemblage 75. The assemblage 75 is diagrammatically shown in Fig. 2, but in greater detail in Fig. 6 and also in Fig. 5.

The assemblage 75 comprises two rings 76 and 77, the ring 76 having offset outer and inner diameters, as at 78, note Fig. 6, to seat in the valve plate 70, thus leaving an annular raised portion, as at 79. The spring ring 77, on the other hand, has a series of circumferential radial indentures, as at 80, note Fig. 5, forming intermediate bowed portions 81. However, when the assemblage is arranged in position, as shown in Fig. 6, the bowed portions 81 are compressed or forced downwardly onto the raised portion 79, thus leaving on the inner diameter of the valve freely flexing portions 82, allowing air to pass freely into the large diameter cylinder upon the suction stroke of the piston 54 and, at the same time, to seal and close the apertures 72 when the piston 54 moves outwardly in the cylinder.

A generally similar type of valve assemblage is indicated at 75" mounted in the head end portion of the piston 54 and retained in position by an apertured valve plate 83 retained in position in the head end of the piston by a snap ring 84. Here again, the valve assemblage 75 allows air to pass into the chamber 62 of the piston 54 in the outward stroke of the piston and, at the same time, 'to check the air against passage in the reverse direction.

In the outward stroke of the piston 54, the air, under pressure, is forced into the liner 50 beyond the small diameter piston 53, passing through a spring checkvalve 85, which is diagrammatically shown in Fig. 2 and in more detail in Fig. 3.

Considering Fig. 3, it will appear that the head end of the piston 53 has an aperture 86, in which is freely mounted a valve support and guide member 87, the mounting being sufficiently free to provide passage of air through the aperture 86 into the head end of the liner 50 for high compression in the outward stroke of the piston 53.

The valve 85 comprises three thin plates 88 having offset central portions 89. The thickness of these plates 88 is exaggerated in the enlarged showing for sake of clarity. The plates nest snugly one within the other and the number of these plates employed will depend upon the pressures developed in the operation of the apparatus, but it is found that two or three plates will be satisfactory for most operations. The plates are sufiiciently flexible to open for the passage of air into the head end of the cylinder, in which the piston 53 operates, the pressure of this air being controlled by operation of the piston 54. The valve 85 will immediately check in sealing the passage 86 in the power stroke of the piston 53.

The member 87 has a series of outwardly and radially extending circumferentially spaced ribs 90, which fit freely in the bore of the piston 53 for guidance of the coupling rod 91. This rod has a head end 92 engaging a sleeve or bushing 93, which securely supports the valve 85 upon the upper end of the member 87, as clearly seen in Fig. 3.

The member 87 has an extended sleeve portion 94 for guidance of a coil spring 95 seated upon an apertured disc 96 at the lower end of the rod 91, the disc being held in position by a nut and washer structure, as at 97. It will, thus, be apparent that air passing from chamber 62 into chamber 63 through passage 61 is free to pass up through and be discharged from the aperture or passage 86 into the outer or head end of the liner 50, in which the piston 53 operates.

At 98, 98' I have shown a head mounted on the opposed end of the unit 12, the head 98 supporting a ring 99, upon the outer end of the liner 50, the ring 99 having a tapered bore 100, having a contracted discharge end 101. Here again, note Fig. 3 of the drawing. The head 89 has a threaded discharge aperture 102 for reception of a discharge tube or pipe, not shown, for transmitting the high pressure air discharge to a suitable means, where the same is to be utilized.

Transversely to the aperture 102, the head 98 has a bore 103, in which a tubular valve 104 is slidably mounted. A spring 105 is arranged in the head and operatively engages the valve to normally support the bevelled seat 106 thereof, upon the contracted end 101 Of the ring 99. The valve 104 has circumferentially spaced recesses 107 in the periphery thereof, soas to provide transmission of air through the bore 103 to the aperture 102 through the passage 108, the latter being shown in Fig. 2 of the drawing.

By virtue of the arrangement of the units 12, 12' one with respect to the other and the opposed relationship of the crankpins 57, 57, it will appear that, when the pistons of one unit, for example, the unit 12, are in the position shown in Fig. 2, the pistons of the opposed unit 12' would be in a midway position between the full compression ends of the two pistons. In Fig. 2 of the drawing, the piston 53 is illustrated at the terminal end of its high compression stroke,-preparatory to beginning the compression stroke of the piston 54 and, as shown, the valve 104 has been indicated as seated to seal the discharged air, under high pressure, from returning to the cylinder in which the piston 53 operates; thus it will be apparent that, when the crankpin 57 reaches its midway position or, in other words, a position of 90 to that shown in Fig. 1, then the crankpin 57' will be, at the completion of its stroke with the large diameter piston actuated by the crankpin 57', at the outer extremity in its operating cylinder. 7

In another 90 of travel ofthe rotor, the crankpin 57 would assume a position occupied by the crankpin 57, as appearing in Fig. 1 of the drawing, and the piston 54 of the unit 12 would be at the end of its compression stroke and the charge of compressed air will be introduced into the cylinder in which the piston 53 operates. Now then, in moving from this last named position to the position shown in Figs. 1 and 2 of the drawing, the crankpin 57 will actuate the pistons 53, 54 through the suction stroke of the piston 54 and the high compression stroke of the piston 53. In other words, a fresh charge of air will be drawn into the cylinder by the piston 54, preparatory to repeating the above cycle of operation. In this connection, it will be understood that the pistons in the unit 12' will operate in the same manner in ac cordance with the setting, as briefly noted in connection with the above described cycle of operation.

It will be apparent that the sleeve liners 50, 51 actually define the cylinders in which the pistons 53 and 54 operate. For purposes of description, the blade ends 37, 38 and 39, in combination with the apertures 42 and the exposed area of the bore 22 of the cylinder 10, immediately in front of each blade, may be said to define the charge chamber, into which the hydraulic medium, under pressure, is introduced in the drive of the rotor, and by virtue of the eccentric movement of the rotor plates 24, 24' on the blades, the area of the charge chamber in front of each blade is gradually reduced to the point of discharge of the hydraulic medium from the discharge or exhaust port, thereby providing highly eflicient hydraulic operation of the rotor.

In connection with the lubrication, it will appear that there will be a certain amount of distribution of oil along surfaces of the blades, which will extend to the apertures 27 of the discs 24, 24, thus will be admitted to enter the lubricating ports 59, 59 through apertures 109 in the discs 24, 24', as will clearly appear from a consideration of Fig. 2 of the drawing. This lubrication will also find its way to the ball bearings 68, 68, as will be apparent.

While the valves 75, 75 and 85 have been generally referred to as check valves, they probably can be better termed as feather control valves, as they, in a checking fashion, simply check against losses when pressure is exerted upon the same, but they flex freely for admission and passage of air therethrough, in the manner previously set forth. At this time, it is also pointed out that the assemblages 52 are sometimes known as two-stage compressor assemblages, in other words, a high and low pressure stage of operation or functioning.

It will also be apparent that, where reference has been made to the several blades, these are sometimes referred to as vanes and, as will be apparent, are double ended vanes fitted for proper and efficient operation in the rotor cylinder, as previously stated being collectively ground for this accurate fitting.

A compressor of the type and kind defined can be economically produced by virtue of the simplicity in the structure of the apparatus and this apparatus will be highly eflicient in operation in producing a predetermined or required source of high pressure air for any use whatever.

i For purposes of description, the liners 51-50 may be said to define large and small diameter cylinders.

Having fully described my invention, what I claim as new and desire to secure by Letters Patent is:

l. A hydraulically actuated air compressor apparatus of the class described, comprising a rotor cylinder, a pair of similar air compressing cylinder units arranged one upon each of opposed sides of the rotor cylinder, said units having housing portions and head ends, each unit including a piston assemblage comprising large and small diameter pistons operating in large and small diameters cylinders, a rotor eccentrically operating in said rotor cylinder, a plurality of blades mounted in said rotor, said rotor cylinder having an admission port for introduction of a hydraulic medium under pressure and a discharge port spaced greater than from said admission port, crankpins movably coupled directly in opposed surfaces of said rotor and operatively engaging the piston assemblages for driving said assemblages in rotation of said rotor, said crankpins operating in the housing portions of said units, said units outwardly and around the housing portions having air passages, ports for placing said air passages in communication with head ends of the cylinder units, in which the large diameter pistons operate, check valves in said last named heads for controlling suction of air into the large diameter cylinders, check valves in the head ends of the large diameter pistons for transmission of air into the small diameter pistons and into the cylinders in which the small diameter pistons operate, check valves in the head ends of the small diameter pistons for controlling pressure discharge of air through said small diameter pistons, and spring seated valves in the heads of the small diameter cylinders for controlling pressure discharge of air to a source of supply by pressure actuation of said small diameter pistons.

2. A structure as defined in claim 1, wherein the rotor includes circumferentially spaced apertures, in which outer extremities of the blades freely operate, and said apertures including offset angmlar portions exposing greater areas of the working surfaces of the blades to the hydraulic pressure medium introduced into the rotor cylinder.

3. A structure as defined in claim 2, wherein said blades include interfitting and nesting central portions.

4. A structure as defined in claim 2, wherein the outer extremity of one end of each blade is offset with respect to the extremity at the other end thereof.

5. A structure as defined in claim 4, wherein one surface of each extremity is in common radial alinement.

6. A structure as defined in claim 1, wherein bearing facing plates are disposed between side surfaces of the rotor cylinder and said units.

7. A structure as defined in claim 6, wherein the rotor comprises two substantially similar rotor discs having openings on adjacent surfaces for operation of central portions of the blades therein.

8. A structure as defined in claim 7, wherein the crankpins include ball ends freely operating in the discs of said rotor.

9. A structure as defined in claim 8, wherein the crankpins operate in tapered bearings supported in central bearing portions of said piston assemblages.

10. A hydraulically actuated air compressor apparatus of the class described, comprising a cylinder, a hydraulically actuated rotor mounted in said cylinder, said rotor actuating crankpins projecting at opposed sides of the rotor, each. crankpin having a ball and socket mounting directly in the rotor, each crankpin operatively engaging and actuating an; air compressor unit, said units being mountedonopposed sides of said cylinder, and the. unit, at one side. of the rotor, being arranged angularly to the unit on the opposed side of the rotor.

11. A structure as defined in claim 10, wherein each unit comprises a low compression and a high compression end, and. check valves for. controlling admission of air into the low compression endv of the unit, transmission ofv air to the high compression end of the unit and discharge of high compressed air from the high compression end of said unit to a source of supply.

12. A structure as defined in claim 11, wherein the low compression end of each unit comprises a. large diameter piston, the high. compression end of the unit including. a. small. diameter piston, and both pistons, at their outer ends, supporting one of. said check valves.

13. A structure as defined in claim 12, wherein said pistons: of. each unit. operate in. cylinders having heads at the ends thereof, and the head ends of. each cylinder including other of said check valves.

14. A structure as defined in claim 10, wherein each unit comprises a piston assemblage comprising small and large diameter pistons, one unit being angular to and crossing the other unit, and the central portion of the assemblage having a bearing for support of the crankpm.

15. A structure as defined in, claim 14, whereinthe rotor, comprises. a pair of discs, eccentrically operating in a hydraulic cylinder, and a plurality of interfitting blades. arranged between said discs and having blade ends operating in peripheral apertures in said discs.

16. A structure, as defined, in claim 15, wherein the apertures of said discs have enlargements offset on one surface, only of each, of said. blade ends.

17. A structure as define in claim 16, wherein the ball end mountings of said crankpins in the discs of said rotor are arranged at. 180 with respect to each other.

References Cited in the file of this patent UNITED STATES PATENTS 1,074,326 Johnson Sept. 30, 1913 1,333,774- Pedersen Mar. 16, 1920 1 ,943,664 Fear Jan. 16, 1934 2,073,215 Mann Mar. 9, 1937 2,256,926 Maniscalco Sept. 23, 1941 2,422,789 Latham June. 24, 1947 2,632,399 Hyre Mar. 24, 1953 FOREIGN PATENTS 80,008 France. Mar. 28, 1868 

